Heat exchanger for solid-state electronic devices

ABSTRACT

A microscopic laminar-flow heat exchanger, well-suited for cooling a heat generating device such as a semiconductor integrated circuit, includes a plurality of thin plates, laminated together to form a block. Each plate has a microscopic recessed portion etched into one face of the plate and a pair of holes cut through the plate such that when the block is formed, the holes align to form a pair of coolant distribution manifolds. The manifolds are connected via the plurality of microscopic channels formed from the recessed portions during the lamination process. Coolant flow through these channels effectuates heat removal.

CROSS REFERENCE TO RELATED APPLICATIONS

This is a division of U.S. Ser. No. 07/679,529, filed Apr. 2, 1991 nowU.S. Pat. No. 5,125,451.

FIELD OF THE INVENTION

This invention relates generally to the field of heat exchangingdevices; particularly to devices and methods aimed at removing heat fromsolid-state electronic circuits and the like.

BACKGROUND OF THE INVENTION

Ever since the integrated circuit was first introduced several decadesago, there has been a continuing effort in the related fields ofsemiconductor processing and integrated circuit design to scale devicesizes downward. Of course, the purpose of this effort has been toincrease total circuit density. Today, the density of components in verylarge scale integrated circuits (VLSI) is so enormous that furtherscaling of circuit components is constrained in part by thermalconsiderations. In other words, heat dissipation and removal have nowbecome an important physical problem which influences the performanceand design of most modern computer systems.

By way of example, the heat generated by a single high-speedemitter-coupled-logic gate (ECL) is typically on the order of a fewmilliwatts. Other logic families such as complementary metal-oxidesemiconductor (CMOS) logic dissipate energy at reduced levels.Unfortunately, when hundreds of thousands of these logic gates arefabricated together on a single integrated circuit the total powerconsumption can easily reach the kilowatt level, especially ifhigh-performance logic gates are used.

Even if a low-power logic family is used, a complete digital computersystem may include tens of millions of transistors fabricated onhundreds of individual semiconductor chips. Because these chips areoften packed closely together to minimize signal propagation delay, itis not uncommon for a computer system to generate tens or hundreds ofkilowatts. At these power levels the operating temperature of theintegrated circuits themselves can rise well above 120 degrees Celsius;such temperatures can cause serious reliability problems. Consequently,the use of various devices such as heat sinks, fans, special materials,etc., is necessary to alleviate the heat dissipation problem.

Addressing this problem, U.S. Pat. Nos. 4,450,472, 4,573,067 ofTuckerman et al., and 4,567,505 of Pease et al., each describe a heatsink in which microscopic heat fins are formed into the backside of asemiconductor substrate. The top surface of the substrate houses anintegrated circuit. According to Tuckerman, the heat fins are fabricatedintegrally--into the semiconductor die itself--employing such techniquesas chemical etching, laser scribing, reactive ion etching,electro-plating, or ultra fine sawing of the backside of the silicondie. Water is then pumped through these slots to provide a laminar flowwhich cools the die.

Theoretically, Tuckerman's approach does provide a means for efficientlyremoving heat from an integrated circuit. However, from a practicalstandpoint, his method suffers from a number of very significantdrawbacks. Foremost among these is the fact that it is highly infeasibleto form microscopic thin channels or slots (of the type required byTuckerman) into the backside of a semiconductor material. Sawing thinslots into a weak, brittle, and hard material such as silicon oftenresults in breakage and other irregularities. In addition, relying onintegrally formed slots limits the height of the cooling channels toroughly the thickness of the silicon wafer. To overcome this latterlimitation, high pressure is needed to force the coolant through theslots at a sufficiently high coolant flow rate so as to provideacceptable heat removal.

Moreover, it should be noted that the fabrication of precise microscopic(on the order of 50 microns wide or less) fins with high enough aspectratios (depth versus width) is a difficult and complex process to carryout. A further problem arises out of the fact that engaging thesemiconductor substrate with a hydrated coolant invariably subjects thesilicon die to unwanted contaminants and impurities. Contamination ofthe substrate may ultimately compromise the reliability of theintegrated circuit.

Therefore, what is needed is an heat exchanger which is more practical,less costly, and involves less complex manufacturing steps than theprior art approach described above. The heat exchanger should be capableof satisfying the heat removal requirements of high-speed switchingcircuitry in a simple, cost-effective manner--without jeopardizing theintegrity of the device.

SUMMARY OF THE INVENTION

The present invention describes a microscopic laminar-flow heatexchanger and process for fabricating the same. The heat exchanger ofthe present invention is ideally suited for cooling a heat generatingdevice such as a semiconductor integrated circuit.

The heat exchanger itself comprises a plurality of thin plates whichhave been laminated together to form a block. In one embodiment, theplates comprise thin copper foil strips each having a microscopicrecessed portion etched into one face of the plate. These recessedportions are chemically etched to a shallow dimension on the order of 50microns deep prior to lamination.

Either before or after the plates are laminated together, holes are cutthrough the plates at opposite sides of the recessed portions such thatwhen the stack is laminated the holes align to form a pair of coolantdistribution manifolds. Each of the manifolds is essentially a tubewhich penetrates into the block. The tubes are connected via theplurality of microscopic channels formed from the recessed portionsduring the lamination process. Optimizing the thickness of the channelsand the coolant flow rate therein allows the block to function as ahighly efficient heat exchanger. The semiconductor die is simply placedor bonded onto the surface of the block to effectuate heat removal.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention and objects and features thereof will be more readilyapparent from the following detailed description and appended claimswhen taken with the drawings, in which:

FIG. 1 is a perspective view of a thin plate, including a recessedportion, employed in conjunction with the present invention.

FIG. 2 is a perspective view of a plurality of individual plates asshown in FIG. 1 following lamination to form a block.

FIG. 3 illustrates a perspective view of the currently preferredembodiment of the present invention. The heat exchanger is shown beingemployed to remove heat from a semiconductor integrated circuit.

FIG. 4 is a side view of an individual plate used in an alternativeembodiment of the present invention. The plate includes a baffledrecessed portion.

FIGS. 5A and 5B are cross-sectional views of an elongated ribbonutilized in an yet alternative embodiment of the present invention.

FIG. 6 is a top view of an alternative embodiment of the presentinvention wherein the ribbon of either FIGS. 5A or 5B is wrappedspirally around itself to create a core.

FIG. 7 is a cross-sectional view taken from the core shown in FIG. 6.

DESCRIPTION OF THE PREFERRED EMBODIMENT(S)

An ultracompact laminar-flow heat exchanger for cooling a heatgenerating device is disclosed. In the following description, numerousspecific details are set forth, such as particular dimensions,materials, structures, etc., in order to provide a thoroughunderstanding of the present invention. However, it will be obvious toone skilled in the art that the invention may be practiced without thesespecific details. In other instances, well-known elements have not beenshown or described in detail to avoid unnecessarily obscuring thepresent invention.

With reference to FIG. 1, a perspective view is shown of a plate member10. In accordance with the currently preferred embodiment, plate 10comprises a thin copper foil having a face 11 into which has been etcheda recessed region 12. The depth of recessed region 12 is preferablyabout 50 microns deep. Located within the recessed region 12 are holes14 and 15, respectively positioned at opposite ends of the recessedarea. The functional importance of recessed region 12 and holes 14 and15 will be explained shortly.

Referring now to FIG. 2, there is illustrated a plurality of identicalplates 10 which have been laminated together to form a block 18. Notethat the location of holes 14 and 15 is consistent among plates 10 suchthat upon lamination, the alignment of holes 14 and 15 create a pair oftubes or manifolds formed through the interior of block 18.

The respective manifolds are connected together within the interior ofblock 18 by means of the microscopic channels formed by recessed regions12. These connecting channels are create during the lamination process,wherein the face 11 of each of the respective plates 10 is pressedagainst the backside of its neighboring plate. The manifolds or tubesand the microscopic channels collectively provide a means for supplyingand distributing a coolant fluid (e.g., water) throughout the interiorof block 18.

Note that the manifolds do not extend completely through block 18.Instead, a special endplate 19 is utilized to contain the coolant fluidwithin the microscopic channels located within the interior of block 18.Endplate 19 also includes a recessed region 12 which is identical tothat associated with plates 10; however, it does not include holes 14 or15. Thus, coolant fluid entering through the input manifold formed byholes 15 remains confined within block 18 as it flows through themicroscopic channels, to be ultimately output through the outputmanifold formed by the alignment of holes 14.

It should be appreciated that lamination is only one of many possiblemethods of forming block 18 out of individual plates 10. For instance,plates 10 may be bonded, glued, soldered, or attached to one another bysome alternative means during this stage of the manufacturing process.The only strict requirement is that when assembled, block 18 must becompletely sealed for purposes of facilitating laminar coolant flow.That is, coolant fluid entering in through the input manifold should notleak or otherwise penetrate through to the exterior of block 18 as itflows through the microscopic channels on its way to the outputmanifold. Hence, a variety of well-known bonding or lamination means maybe used for this purpose.

The choice of material which makes up plates 10 is also an optionalconsideration. Although a material having a high thermal conductivitysuch as copper is preferred, alternative materials may be better suiteddepending on the particular application, or on the type of heatgenerating device that the exchanger will be used in conjunction with.For example, in certain instances it may be desirable to manufactureplates 10 out of a material having a thermal coefficient of expansionwhich closely matches that of the heat generating device to which itwill be affixed.

A perspective view of the completely manufactured heat exchanger of thecurrently preferred embodiment of the present invention is shown in FIG.3. As part of the manufacturing process, once plates 10 have beenlaminated together to form block 18 and endplate 19 has been attached, acover plate 22 is likewise attached to the front side of block 18.Actually, the entire block, including end plate 19 and cover plate 22,may be assembled as part of a single lamination step. (Really, there isno significance to attaching cover plate 22 after block 18 and endplate19 have been assembled).

Cover plate 22 essentially performs the same function as does endplate19. It should be apparent that the purpose of cover plate 22 is toconfine the flow of coolant within the microscopic channels to theinterior of block 18. It performs this function in exactly the same waythat endplate 19 does. Note, however, that there is no specificrequirement for cover plate 22 to have a recessed portion 12, as waspreviously shown in connection with plates 10. But cover plate 22 musthave corresponding holes 14 and 15 to allow attachment of respectivepipes 25 and 24, as shown in FIG. 3.

Pipes 24 and 25 provide a means for distributing coolant uniformlythroughout the interior of block 18. By way of example, in normaloperation a coolant fluid such as water is pumped into input pipe 24 inalignment with holes 15 of individual plates 10. After the coolantenters block 18, the coolant engages the microscopic channels in alaminar flow to effectuate heat removal. The direction of coolant flowwithin these microscopic channels is shown in FIG. 3 by arrow 26. Aftertraversing the length of the microscopic channels formed by the recessedregions 12, the coolant exits output pipe 25.

Depending on the type of system in which the heat exchanger of FIG. 3 isemployed, output pipe 25 may be coupled to a refrigeration unit, or somesimilar means of re-cooling the fluid prior to delivering it back againto input pipe 24. Note that FIG. 3 further illustrates, by way ofexample, how a semiconductor die 20 may be affixed to the top of theheat exchanger during normal use. The integrated circuit fabricated onthe surface of die 20 is represented in FIG. 3 by dashed line 21.

It is important to understand that in the embodiment of FIG. 3, pipes 24and 25 typically penetrate no further than the thickness of cover plate22. As a consequence--depending on the strength and durabilityrequirements of the heat exchanger--cover plate 22 may be manufacturedto be slightly thicker. Another option is to manufacture plate 22 out ofa different, more rigid, material than the rest of the block.

Still another alternative is to manufacture the heat exchanger of FIG. 3so that pipes 24 and 25 penetrate into the interior of block 18 in sucha way as to provide added durability and strength. However, for thislater case it should be understood that pipes 24 and 25 would have toinclude a single elongated slot in the pipe that aligns with the coolantchannels, or alternatively, a series of macroscopic openings that wouldallow the coolant to pass from the manifold into the microscopicchannels, and vice-a-versa. Of course, these openings must be alignedwith the microscopic channels so that coolant flow could take place.

One key aspect of the present invention is the depth of recessedportions 12 formed on face 11 of plates 10. Ideally, the depth of therecessed region is made to be about twice the thickness of the thermalboundary layer associated with the particular coolant employed. Thiscondition provides the maximum heat transfer from the plate surface tothe coolant fluid, and allows the maximum number of channels to beformed per square inch.

Obviously, any increase in the channel density (i.e., the number ofchannels per square inch) within block 18 enhances the heat removingproperties of the present invention. In the currently preferredembodiment, individual plates 10 are approximately 0.125 millimetersthick, whereas the recessed portions are etched to a depth ofapproximately 50 microns using an ordinary chemical etchant. Holes 14and 15 may assume a variety of shapes and sizes, however, currently thediameter of these holes is approximately 8 millimeters.

Practitioners in the art will appreciate that the recessed portions maybe formed by some means other than chemical etching. For example, wherea relatively soft metal such as copper is utilized, the required recessfeature may be simply stamped or pressed into the face of the plate. Instill other embodiments, a series of flat plates in alternate positionwith a sequence of frame members may be utilized. For this latter case,the frame members themselves provide the required channel spacingbetween the flat plates. Other embodiments which achieve the samepurpose of forming microscopic channels within a thermally conductiveblock are also possible. Such alternative embodiments are considered tobe well within the spirit and scope of the present invention.

As an example of the multifarious alternations which may be made uponthe basic invention, FIG. 4 shows one way in which turbulence may beintroduced into the coolant flow within the interior of the heatexchanger. FIG. 4 represents a side view of a plate 10 similar to theones previously discussed. As before, plate 10 includes a recessedportion 12, a face 11 and holes 14 and 15. But the plate of FIG. 4further includes finger members 31 which extend into the recessed region12. Yet finger members 31 remain co-planar with face 11. For instance,if recessed region 12 are formed by chemical etching, finger members 31may be easily fabricated by proper patterning of the recessed regionprior to the etching process.

The purpose of finger members 31 is to disrupt the normal laminar flowof coolant through the microscopic channels. As can be seen by thesinuous arrow passing through recessed region 12 of FIG. 4, the coolantis forced to flow a greater distance before reaching the output manifoldregion. The increased distance which the coolant fluid musttraverse--coupled with the effects of an intentionally inducedturbulence--will provide more efficient heat transfer within the heatexchanger for certain embodiments.

The nature of the actual improvement in heat transfer efficiency willdepend on such factors as the type of material comprising plates 10, thetype of coolant fluid, the thickness of the channels, the velocity ofthe coolant, etc. The specific nature of the baffling members (e.g., theshape, spacing, length, etc., of fingers 31) will also influence theefficiency of the heat removal process. Hence, each of these factors ispreferably optimized to yield the most efficacious heat transfermechanism possible. (Note that the baffling pattern shown in FIG. 4 isfor illustration purposes only--it being appreciated that numerous otherpatterns and configurations are available to one of ordinary skill inthe art.)

FIGS. 5 through 7 illustrate an alternative embodiment of the presentinvention in which coolant flows radially throughout a circular coremember. Rather than laminating a plurality of distinct plates togetherto form a block, the alternative embodiment of FIGS. 5-7 is comprised ofa single, thermally conductive ribbon which has been wrapped spirallyagainst itself to form a circular core.

FIGS. 5A and 5B show cross sectional views of two possible ribbons 34and 36, respectively. Ribbon 34 has a cross-sectional view whichresembles an I-bar, while ribbon 36 assumes the shape of a three-sidedrectangle. Regions 35 and 37 on either side of respective ribbons 34 and36 correspond to the recessed portion 12 of the previously discussedembodiments. This means that regions 35 and 37 may be formed by suchprocesses as chemical etching, stamping, etc.

Once ribbon 34 (or 36) has been spirally wrapped around against itselfand laminated into a single core 40, regions 35 (or 37) define a spiralmicroscopic channel which continuously winds throughout the center ofcore 40 (see FIG. 6). The formation of these microscopic channels isdepicted by the radial cross-sectional cut view of core 40 appearing inFIG. 7.

By viewing FIG. 7, one can easily see how the microscopic channelregions 35 are formed as a result of continuously wrapping ribbon 34against itself. The end effect is as if a series of I-bar members werestacked against one another, side-to-side. Note that within core 40, theside surfaces 46 of ribbon 34 abut each other in the same manner thatplates 10 are joined together to form the microscopic channels withinblock 18. Just as was the case in forming block 18, core 40 may beformed by any sealing process of ribbon 34 which confines the coolantflow within channels 35.

Referring back to FIG. 6, a top view of core 40 shows two holes 47 and48 penetrating core 40 from opposite ends. These holes provide thecoolant distribution manifold means for the heat exchanger of FIG. 6. Inother words, tubes 41 and 42 are attached to the ends of holes 47 and48, respectively, so the coolant fluid may pass through the microscopicchannels in parallel fashion radially about core 40 as shown by arrows44.

It is crucial to understand that holes 47 and 48 do not extend fullythrough to the center of core 40. Their penetration must stop short ofthe center to insure that coolant flow takes place radially through themicroscopic channels--and not directly (i.e., bypassing the channels)from the input to the output manifold tubes. Also note that theembodiment of FIG. 6 has similar requirements for sealing the ends ofcore 40. In other words, the two ends, 38 and 39 of ribbon 34, must besealed in some manner to confine the coolant fluid within core 40.

FIG. 5 shows an alternative ribbon 36 which, instead of including a pairof recessed regions, has a single recessed region 37. Optimally, thedepth of region 37 is approximately equal to twice the thermal boundarylayer thickness (twice the depth of recessed portion 35). Duringmanufacturing, ribbon 36 is spirally wrapped in the same way asdescribed previously in connection with ribbon 34 of FIG. 5A. However,due to its different cross-sectional shape, the core formed by ribbon 36may require a different sealing means at ends 38 and 39. Laminar coolantflow in core 40 is identical for either of ribbons 34 or 36.

I claim:
 1. A heat exchanger for cooling a heat generating devicecomprising:an elongated ribbon having first and second sides, at leastsaid first side including a microscopic recessed area, said ribbon beingspirally wrapped into a core element such that said first and secondsides abut each other to create enclosed microscopic channels throughoutsaid core; coolant manifold means for flowing a coolant fluid throughsaid enclosed microscopic channels in parallel fashion said device beingcooled when placed in contact with said core element.
 2. The heatexchanger of claim 1 wherein said core element comprises a materialhaving a high thermal conductivity.
 3. The heat exchanger of claim 2wherein said core element comprises copper.
 4. The heat exchanger ofclaim 2 wherein said coolant manifold means comprises:an intake manifoldfor applying said coolant to a first side of said enclosed microscopicslots; an exhaust manifold for removing said coolant from a second sideof said slots; and means for pumping said coolant through said slots ina direction from said intake manifold to said exhaust manifold.
 5. Theheat exchanger of claim 4 wherein said intake and exhaust manifolds eachcomprise a tube fitted within a hole in said core element which providesan opening to said enclosed microscopic slots.
 6. The heat exchanger ofclaim 5 wherein the width of each of said channels is approximatelytwice the thermal boundary layer thickness.
 7. The heat exchanger ofclaim 6 wherein said coolant is distributed uniformly through saidenclosed slots.
 8. The heat exchange of claim 7 further comprisingbaffling means for altering the flow of said coolant within said slotsproviding more efficient heat transfer between said coolant and saidcore element.
 9. The heat exchanger of claim 8 wherein said recessedportions are approximately 50 microns deep.
 10. The heat exchanger ofclaim 9 wherein said recessed portions are centrally located along saidat least one face of said plates such that the flow of said coolant isconfined within the interior of said core element.
 11. The heatexchanger of claim 10 wherein said heat generating device comprises asemiconductor substrate upon which is fabricated an integrated circuit.